US20170009805A1 - Tilting Segment For A Shaft Bearing Device, And Shaft Bearing Device - Google Patents
Tilting Segment For A Shaft Bearing Device, And Shaft Bearing Device Download PDFInfo
- Publication number
- US20170009805A1 US20170009805A1 US15/113,685 US201515113685A US2017009805A1 US 20170009805 A1 US20170009805 A1 US 20170009805A1 US 201515113685 A US201515113685 A US 201515113685A US 2017009805 A1 US2017009805 A1 US 2017009805A1
- Authority
- US
- United States
- Prior art keywords
- segment
- groove
- tilting
- extending
- axial direction
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/107—Grooves for generating pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C37/00—Cooling of bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C37/00—Cooling of bearings
- F16C37/002—Cooling of bearings of fluid bearings
Definitions
- the invention is directed to a tilting segment for a shaft bearing device and a shaft bearing device.
- a shaft bearing device for slide bearing support of a rotating shaft comprising a bearing base body and a plurality of tilting segments received at the bearing base body and positioned one behind the other in circumferential direction is known from U.S. Pat. No. 6,361,215 B1.
- Each of the tilting segments has a slide bearing face bounded on one side by a segment leading edge extending in axial direction and a segment trailing edge extending likewise in axial direction and on the other side by lateral edges extending in circumferential direction between the segment leading edge and the segment trailing edge. It is further known from U.S. Pat. No.
- 6,361,215 B1 that a so-called directed lubrication or a so-called grooved lubrication can be used at a shaft bearing device of this type.
- the grooved lubrication has the advantage of a better damping of vibrations, while directed lubrication has the advantage of lower oil consumption and, therefore, lower power loss.
- a groove extending in axial direction, or leading edge groove as it is called, via which the tilting segment is supplied with oil is provided according to U.S. Pat. No. 6,361,215 B1 at the start of the slider surface of the tilting segment adjacent to the segment leading edge.
- grooves which extend in circumferential direction, run adjacent to the lateral edges and extend up to the region of the trailing edge of the tilting segment.
- a further shaft bearing device with tilting segments is known from U.S. Pat. No. 6,485,182 B1. According to this prior art, the tilting segments are supplied with oil via a gap formed between adjacent tilting segments.
- the shaft bearing devices with tilting segments known from the prior art have the problem that the tilting segments, which are loaded relatively lightly in operation, have a tendency toward segment flutter, as it is called.
- Segment flutter describes subsynchronous vibrations induced in the bearing itself. These subsynchronous vibrations occur as a result of the continuous oscillation of the unloaded tilting segments between two different balance points.
- the tilting segment cannot occupy a stable position and is therefore unstable.
- Segment flutter can occur, for example, as a result of deficient lubrication. This is the case when the lubricating gap cannot be completely filled with lubricant. This can occur when the eccentricity between the center point of the shaft and the center point of the bearing is very great.
- the lubricating gap widths between the unloaded tilting segment and loaded tilting segment can deviate greatly from one another so that the amount of lubricant supplied can no longer completely fill the highly enlarged lubricating gap of the unloaded tilting segment.
- segment flutter leads to solid contact between the segment sliding face and the shaft surface and thus to damage or even destruction of the segment.
- One possibility for reducing segment flutter consists in outfitting the bearing with a grooved lubrication so that the entire bearing is filled with lubricant.
- a lateral seal is usually inserted at the axial bearing ends of the bearing housing that restricts the lateral flow of lubricating oil that is heated via the tilting segment out of the bearing housing. Accordingly, the lubricating film temperature is appreciably higher owing to the restricted outflow of warm lubricating oil from the slide bearing and, further, the power loss is also appreciably higher because of the increased fluid friction.
- Mechanical adjustments of this type for suppressing or reducing segment flutter are very costly.
- a groove that extends in axial direction and that is located nearer to the segment trailing edge than it is to the segment leading edge is incorporated in the slide bearing face.
- the height of the gap between tilting segment and the shaft supported by this shaft bearing device becomes narrower in vertical direction from the base of the axially extending groove to the slide bearing face that extends up to the segment trailing edge. Because of this narrowing of the gap and due to a difference in velocity between shaft and bearing and because the lubricant adheres to the shaft surface, there results a buildup of hydrodynamic pressure.
- the built-up hydrodynamic pressure causes the gap between tilting segment and shaft to be filled with lubricant in the divergent gap area between this tilting segment and this shaft. Accordingly, a heat exchange also takes place between the differently hot layers of lubricant between the shaft and tilting segment.
- the transfer of heat in the region of the shaft surface is substantially improved through the partial transition into the turbulent flow regime with a corresponding increase in the Nusselt number (Nu), and Taylor vortices directed in circumferential direction are also partially generated and likewise lead to an improved heat transfer, and the shaft temperature and temperature level of the bearing accordingly decrease overall.
- Nusselt number Nusselt number
- a longitudinal central axis of the groove extending in axial direction is positioned in a portion of the slide bearing face located at between 60% and 90%, preferably between 60% and 80%, particularly preferably between 70% and 80%, of the circumferential extension U 1 of the slide bearing face. Segment flutter can be countered in a particularly advantageous manner in this way.
- This step is also advantageous for suppressing segment flutter at a tilting segment of a shaft bearing device.
- a circumferentially extending groove that extends into the axially extending groove proceeding from the segment leading edge is introduced into the slide bearing face.
- Oil can be conveyed into the axially extending groove proceeding from the segment leading edge through the groove extending in circumferential direction.
- the oil conveyed into this axially extending groove is heated to a lesser extent than the oil conveyed in circumferential direction from the segment leading edge to the sliding surface. Therefore, owing to the additional back-up of oil resulting from the hydrodynamic pressure, a heat exchange takes place between the differently heated oil flows in the divergent gap area. This likewise leads to the cooling of the shaft surface and to reduction of the temperature level in the shaft bearing device overall.
- the hydrodynamic pressure ratios that are formed not only can segment flutter be counteracted but, further, pronouncedly laminar hot oil layers at the shaft surface can be broken up.
- the grooves in the invention do not serve to hold back hot oil in the slide bearing for filling the divergent gap; rather, as a result of the tilting segment according to the invention, the hot oil is allowed to flow out of the slide bearing and the temperature level in the bearing can be decreased.
- the groove extending in axial direction can have a bevel, specifically such that, viewed in circumferential direction, a groove depth of the groove extending in axial direction increases in direction of the segment trailing edge. Pronouncedly laminar hot oil layers can also be broken up in this way and turbulent oil flows and Taylor vortices running in the rotating direction of the shaft can be generated to improve the removal of heat from the shaft.
- FIG. 1 is a schematic view of a shaft bearing device viewed axially;
- FIG. 2 is a perspective view of a first tilting segment according to one aspect of the invention for a shaft bearing device
- FIG. 3 is a perspective view of a second tilting segment according to one aspect of the invention for a shaft bearing device
- FIG. 4 is a perspective view of a third tilting segment according to one aspect of the invention for a shaft bearing device.
- FIG. 5 is a perspective view of a fourth tilting segment according to one aspect of the invention for a shaft bearing device.
- the present invention is directed to a shaft bearing device for slide bearing support of a rotating shaft and to a tilting segment for a shaft bearing device of this type.
- FIG. 1 shows, looking axially, a shaft bearing device 10 for the slide bearing support of a rotating shaft 13 , wherein the shaft bearing device 10 has a bearing base body 11 comprising two partial rings 11 a, 11 b in which a plurality of tilting segments 12 are received one behind the other viewed in circumferential direction.
- the tilting segments 12 are arranged radially outwardly in circumferential direction around the shaft 13 to be supported.
- FIG. 2 shows a perspective view of an embodiment form of a tilting segment 12 for a shaft bearing device 10 of this type according to a first variant of the invention.
- the tilting segment 12 has a base body 15 that forms a slide bearing face 16 .
- the slide bearing face 16 is bounded by a segment leading edge 17 extending in axial direction, a segment trailing edge 18 likewise extending in axial direction, and by lateral edges 19 , 20 extending in circumferential direction between the segment leading edge 17 and the segment trailing edge 18 .
- the segment leading edge 17 is that edge of the base body 15 of the tilting segment 12 that extends in axial direction and is positioned in front when viewed in the rotating direction of the shaft 13 to be supported.
- the segment trailing edge 18 is positioned in back when viewed in the rotating direction of the shaft 13 to be supported.
- the rotating direction of the shaft to be supported is designated by arrow 21 in FIG. 2 .
- a groove 22 extending in axial direction is introduced into the slide bearing face 16 in a portion of the slide bearing face 16 that is nearer to the segment trailing edge 18 than it is to the segment leading edge 17 .
- the tilting segment 12 is loaded by forces in operation, and that portion of the slide bearing face 16 of the tilting segment 12 in which the highest forces occur at the respective tilting segment 12 in operation is designated as main load zone of the respective tilting segment 12 .
- the groove 22 extending in axial direction is positioned between this main load zone and the segment trailing edge 18 viewed in circumferential direction.
- oil collects in the axially extending groove 22 positioned nearer to the segment trailing edge 18 than to the segment leading edge 17 so that an additional hydrodynamic pressure is built up in operation which causes a preloading for the respective tilting segment 12 .
- Segment flutter at the respective tilting segment 12 can be suppressed in this way.
- the axially extending groove 22 inserted into the slide bearing face 16 is positioned nearer to the segment trailing edge 18 than it is to the segment leading edge 17 , namely between the main load zone of the tilting segment 12 and the segment trailing edge 18 thereof.
- a longitudinal central axis of the axially extending groove 22 is positioned in a portion of the slide bearing face 16 lying at between 60% and 90%, preferably between 60% and 80%, particularly preferably between 70% and 80%, of the circumferential extension U 1 of the slide bearing face 16 .
- the ratio is 0.02 ⁇ VU ⁇ 0.20, preferably 0.05 ⁇ VU ⁇ 0.20, particularly preferably 0.05 ⁇ VU ⁇ 0.10.
- a groove 22 with a groove width U 2 of this kind has proven particularly advantageous for suppressing segment flutter.
- the groove 22 extending in axial direction is bounded by four groove walls, namely by a first groove wall 23 which extends in axial direction and faces the segment trailing edge 18 , a second groove wall 24 which likewise extends in axial direction and is remote of the segment trailing edge 18 , and by two lateral groove walls 25 , 26 which extend between the first groove wall 23 and the second groove wall 24 .
- the distance between the first groove wall 23 and the second groove wall 24 each of which extends in axial direction, determines the groove width U 2 of groove 22
- the distance between the lateral groove walls 25 , 26 determines an axially extending groove length L 2 of the groove 22 extending in axial direction.
- the axially extending groove 22 which is formed at the slide bearing face 16 of the tilting segment 12 , is bounded on all sides by groove walls 23 , 24 , 25 and 26 , the groove 22 having a constant groove depth viewed in radial direction.
- FIG. 3 shows a further development of tilting segment 12 from FIG. 2 .
- the variant in FIG. 3 differs from the variant in FIG. 2 in that a further groove 27 is incorporated in the slide bearing face 16 of the tilting segment 12 , namely, a circumferentially extending groove 27 , which extends into the axially extending groove 22 proceeding from the segment leading edge 17 . Oil can be conveyed from the segment leading edge 17 into the axially extending groove 22 via this groove 27 extending in circumferential direction.
- FIG. 4 shows a further development of the invention in which the groove 22 extending in circumferential direction runs adjacent to one of the lateral edges 19 , 20 of the slide bearing face 16 and, in a lateral portion adjacent to a lateral groove wall 25 , runs into the groove 22 extending in axial direction.
- FIG. 5 A further variant of a tilting segment 12 is shown in FIG. 5 .
- the groove 22 extending in axial direction is characterized by a bevel, namely such that proceeding from the groove wall 24 remote of the segment trailing edge 18 , the groove depth of groove 22 increases in direction of the groove wall 23 facing the segment trailing edge 18 .
- the groove depth according to the illustration in FIG. 5 preferably ramps up linearly, i.e., steadily or continuously, in direction of the groove wall 23 facing the segment trailing edge 18 .
- the bevel can also be constructed with a radius.
- the supply of oil into the axially extending groove 22 can be reinforced in this way so as to break up hot oil layers in the region of the shaft surface of the shaft 13 to be supported and, on the other hand, to generate a possible turbulent oil flow and Taylor vortices running in the rotating direction of the shaft 13 to be supported in order in this way ultimately to improve the transfer of heat and, therefore, the removal of heat from the segment 12 and the supported shaft 13 .
- segment flutter of tilting segments 12 can be effectively and reliably countered. Further, the transfer of heat from the lubricating gap can be improved and the temperature level can accordingly be lowered.
- the present invention is directed not only to a tilting segment 12 but also to a shaft bearing device 10 with at least one tilting segment 12 of this kind.
- first tilting segments which may be formed as tilting segments 12
- second tilting segments 12 are more highly loaded by forces than second tilting segments 12 .
- the lower tilting segments 12 in particular are more highly loaded by forces than the upper tilting segments 12 .
- those tilting segments 12 which are loaded relatively lightly by forces, i.e., exclusively at least one of the second tilting segments 12 , are configured in the manner described with reference to FIGS. 2 to 5 .
- all of the second tilting segments which are loaded by forces to an extent below a limiting value are configured as described with reference to FIGS. 2 to 5 .
- the first tilting segments which are loaded by forces to an extent greater than the limiting value are preferably constructed in such a way that no grooves are incorporated in the slide bearing face 16 thereof.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
- This is a U.S. national stage of application No. PCT/EP2015/000123, filed on Jan. 22, 2015. Priority is claimed on German Application No.: DE102014000775.8, filed Jan. 24, 2014, the content of which is incorporated here by reference.
- 1. Field of the Invention
- The invention is directed to a tilting segment for a shaft bearing device and a shaft bearing device.
- 2. Description of the Prior Art
- A shaft bearing device for slide bearing support of a rotating shaft comprising a bearing base body and a plurality of tilting segments received at the bearing base body and positioned one behind the other in circumferential direction is known from U.S. Pat. No. 6,361,215 B1. Each of the tilting segments has a slide bearing face bounded on one side by a segment leading edge extending in axial direction and a segment trailing edge extending likewise in axial direction and on the other side by lateral edges extending in circumferential direction between the segment leading edge and the segment trailing edge. It is further known from U.S. Pat. No. 6,361,215 B1 that a so-called directed lubrication or a so-called grooved lubrication can be used at a shaft bearing device of this type. The grooved lubrication has the advantage of a better damping of vibrations, while directed lubrication has the advantage of lower oil consumption and, therefore, lower power loss. In order to provide a shaft bearing device with lower power loss and reduced vibration behavior at the same time, a groove extending in axial direction, or leading edge groove as it is called, via which the tilting segment is supplied with oil is provided according to U.S. Pat. No. 6,361,215 B1 at the start of the slider surface of the tilting segment adjacent to the segment leading edge. Likewise introduced into the slide bearing face are grooves which extend in circumferential direction, run adjacent to the lateral edges and extend up to the region of the trailing edge of the tilting segment.
- These grooves, which extend in circumferential direction in the tilting segments and which are known from U.S. Pat. No. 6,361,215 B1, reduce the lateral outflow of oil from the respective tilting segment. With this reduced lateral oil flow, a defined amount of oil is conveyed into the divergent lubricating gap at the end of the segment, where it provides for improved vibration damping of possible vibrations known as synchronous vibrations and subsynchronous vibrations.
- A further shaft bearing device with tilting segments is known from U.S. Pat. No. 6,485,182 B1. According to this prior art, the tilting segments are supplied with oil via a gap formed between adjacent tilting segments.
- The shaft bearing devices with tilting segments known from the prior art have the problem that the tilting segments, which are loaded relatively lightly in operation, have a tendency toward segment flutter, as it is called.
- Segment flutter describes subsynchronous vibrations induced in the bearing itself. These subsynchronous vibrations occur as a result of the continuous oscillation of the unloaded tilting segments between two different balance points. The tilting segment cannot occupy a stable position and is therefore unstable. Segment flutter can occur, for example, as a result of deficient lubrication. This is the case when the lubricating gap cannot be completely filled with lubricant. This can occur when the eccentricity between the center point of the shaft and the center point of the bearing is very great. In this case, the lubricating gap widths between the unloaded tilting segment and loaded tilting segment can deviate greatly from one another so that the amount of lubricant supplied can no longer completely fill the highly enlarged lubricating gap of the unloaded tilting segment.
- In extreme cases, segment flutter leads to solid contact between the segment sliding face and the shaft surface and thus to damage or even destruction of the segment.
- One possibility for reducing segment flutter consists in outfitting the bearing with a grooved lubrication so that the entire bearing is filled with lubricant. In this case, with regard to construction, a lateral seal is usually inserted at the axial bearing ends of the bearing housing that restricts the lateral flow of lubricating oil that is heated via the tilting segment out of the bearing housing. Accordingly, the lubricating film temperature is appreciably higher owing to the restricted outflow of warm lubricating oil from the slide bearing and, further, the power loss is also appreciably higher because of the increased fluid friction. Mechanical adjustments of this type for suppressing or reducing segment flutter are very costly.
- Heretofore, there were no known solutions by which so-called segment flutter could be securely and reliably prevented by simple means.
- In view of the foregoing, it is an object of one aspect of the present invention to provide a novel tilting segment for a shaft bearing device and a novel shaft bearing device.
- According to one aspect of the invention, a groove that extends in axial direction and that is located nearer to the segment trailing edge than it is to the segment leading edge is incorporated in the slide bearing face. The invention makes it possible to securely and reliably prevent so-called segment flutter, particularly at relatively lightly loaded tilting segments of a shaft bearing device.
- At the transition from the groove extending in axial direction, the height of the gap between tilting segment and the shaft supported by this shaft bearing device becomes narrower in vertical direction from the base of the axially extending groove to the slide bearing face that extends up to the segment trailing edge. Because of this narrowing of the gap and due to a difference in velocity between shaft and bearing and because the lubricant adheres to the shaft surface, there results a buildup of hydrodynamic pressure.
- Because the axially extending groove lies nearer to the segment trailing edge than it does to the segment leading edge in circumferential direction and since, therefore, the gap narrowing is also nearer to the segment trailing edge than it is to the segment leading edge, the buildup of an additional hydrodynamic pressure takes place in the divergent area between the shaft and the tilting segment. As a result of hydrodynamic pressure being generated in the divergent area, this divergent area between the tilting segment and shaft is filled with lubricant. A complete filling of the divergent area would otherwise only be possible with grooved bearings that prevent lubricant from flowing off laterally. Filling the divergent gap prevents the movement of the tilting segment in direction of the now full divergent gap so that segment flutter is effectively countered.
- The built-up hydrodynamic pressure causes the gap between tilting segment and shaft to be filled with lubricant in the divergent gap area between this tilting segment and this shaft. Accordingly, a heat exchange also takes place between the differently hot layers of lubricant between the shaft and tilting segment.
- In this case, the transfer of heat in the region of the shaft surface is substantially improved through the partial transition into the turbulent flow regime with a corresponding increase in the Nusselt number (Nu), and Taylor vortices directed in circumferential direction are also partially generated and likewise lead to an improved heat transfer, and the shaft temperature and temperature level of the bearing accordingly decrease overall.
- According to an advantageous further development, in direction of the circumferential extension U1 of the slide bearing face starting with 0% at the segment leading edge and ending with 100% at the segment trailing edge, a longitudinal central axis of the groove extending in axial direction is positioned in a portion of the slide bearing face located at between 60% and 90%, preferably between 60% and 80%, particularly preferably between 70% and 80%, of the circumferential extension U1 of the slide bearing face. Segment flutter can be countered in a particularly advantageous manner in this way.
- According to another advantageous further development, the ratio VU=U2/U1 between the circumferentially extending groove width U2 of the groove extending in axial direction and the circumferential extension U1 of the slide bearing face extending between the segment leading edge and the segment trailing edge is 0.02≦VU≦0.20, preferably 0.05≦VU≦0.20, particularly preferably 0.05≦VU≦0.10. These steps also allow segment flutter of a tilting segment to be effectively countered.
- According to another advantageous further development, the ratio VL=L2/L1 between the axially extending groove length L2 of the groove extending in axial direction and the axial extension L1 of the slide bearing face extending between the lateral edges is 0.5≦VL<1.0, preferably 0.6≦VL<1.0, particularly preferably 0.7≦VL<1.0. This step is also advantageous for suppressing segment flutter at a tilting segment of a shaft bearing device.
- Preferably, a circumferentially extending groove that extends into the axially extending groove proceeding from the segment leading edge is introduced into the slide bearing face. Oil can be conveyed into the axially extending groove proceeding from the segment leading edge through the groove extending in circumferential direction. The oil conveyed into this axially extending groove is heated to a lesser extent than the oil conveyed in circumferential direction from the segment leading edge to the sliding surface. Therefore, owing to the additional back-up of oil resulting from the hydrodynamic pressure, a heat exchange takes place between the differently heated oil flows in the divergent gap area. This likewise leads to the cooling of the shaft surface and to reduction of the temperature level in the shaft bearing device overall. As has already been stated, as a result of the hydrodynamic pressure ratios that are formed, not only can segment flutter be counteracted but, further, pronouncedly laminar hot oil layers at the shaft surface can be broken up.
- In contrast to U.S. Pat. No. 6,361,215 B1, the grooves in the invention do not serve to hold back hot oil in the slide bearing for filling the divergent gap; rather, as a result of the tilting segment according to the invention, the hot oil is allowed to flow out of the slide bearing and the temperature level in the bearing can be decreased.
- In addition or preferably as an alternative to the groove extending in circumferential direction, the groove extending in axial direction can have a bevel, specifically such that, viewed in circumferential direction, a groove depth of the groove extending in axial direction increases in direction of the segment trailing edge. Pronouncedly laminar hot oil layers can also be broken up in this way and turbulent oil flows and Taylor vortices running in the rotating direction of the shaft can be generated to improve the removal of heat from the shaft.
- Preferred further developments of the invention are indicated in the subclaims and the following description. Embodiment examples of the invention are described more fully with reference to the drawings without the invention being limited to these embodiment examples. In drawings:
-
FIG. 1 is a schematic view of a shaft bearing device viewed axially; -
FIG. 2 is a perspective view of a first tilting segment according to one aspect of the invention for a shaft bearing device; -
FIG. 3 is a perspective view of a second tilting segment according to one aspect of the invention for a shaft bearing device; -
FIG. 4 is a perspective view of a third tilting segment according to one aspect of the invention for a shaft bearing device; and -
FIG. 5 is a perspective view of a fourth tilting segment according to one aspect of the invention for a shaft bearing device. - The present invention is directed to a shaft bearing device for slide bearing support of a rotating shaft and to a tilting segment for a shaft bearing device of this type.
- In a highly schematic manner,
FIG. 1 shows, looking axially, ashaft bearing device 10 for the slide bearing support of arotating shaft 13, wherein theshaft bearing device 10 has a bearing base body 11 comprising two partial rings 11 a, 11 b in which a plurality of tiltingsegments 12 are received one behind the other viewed in circumferential direction. The tiltingsegments 12 are arranged radially outwardly in circumferential direction around theshaft 13 to be supported. Agap 14 for supplying lubricating oil in direction of the leading edge of the tiltingsegment 12, or front edge in rotating direction of the shaft, and for carrying away hot oil from the trailing edge of the tiltingsegment 12, or back edge in rotating direction of the shaft, is formed between adjacent tiltingsegments 12. -
FIG. 2 shows a perspective view of an embodiment form of a tiltingsegment 12 for ashaft bearing device 10 of this type according to a first variant of the invention. - The tilting
segment 12 has abase body 15 that forms aslide bearing face 16. The slide bearing face 16 is bounded by asegment leading edge 17 extending in axial direction, asegment trailing edge 18 likewise extending in axial direction, and bylateral edges segment leading edge 17 and thesegment trailing edge 18. - The
segment leading edge 17 is that edge of thebase body 15 of the tiltingsegment 12 that extends in axial direction and is positioned in front when viewed in the rotating direction of theshaft 13 to be supported. Thesegment trailing edge 18 is positioned in back when viewed in the rotating direction of theshaft 13 to be supported. The rotating direction of the shaft to be supported is designated byarrow 21 inFIG. 2 . - Within the meaning of the present invention, a
groove 22 extending in axial direction is introduced into theslide bearing face 16 in a portion of theslide bearing face 16 that is nearer to thesegment trailing edge 18 than it is to thesegment leading edge 17. - The tilting
segment 12 is loaded by forces in operation, and that portion of theslide bearing face 16 of the tiltingsegment 12 in which the highest forces occur at therespective tilting segment 12 in operation is designated as main load zone of therespective tilting segment 12. Thegroove 22 extending in axial direction is positioned between this main load zone and thesegment trailing edge 18 viewed in circumferential direction. - In operation, oil collects in the
axially extending groove 22 positioned nearer to thesegment trailing edge 18 than to thesegment leading edge 17 so that an additional hydrodynamic pressure is built up in operation which causes a preloading for therespective tilting segment 12. Segment flutter at therespective tilting segment 12 can be suppressed in this way. - As has already been stated, the
axially extending groove 22 inserted into theslide bearing face 16 is positioned nearer to thesegment trailing edge 18 than it is to thesegment leading edge 17, namely between the main load zone of the tiltingsegment 12 and thesegment trailing edge 18 thereof. In direction of the circumferential extension U1 of theslide bearing face 16 starting with 0% at thesegment leading edge 17 and ending with 100% at thesegment trailing edge 18, a longitudinal central axis of theaxially extending groove 22 is positioned in a portion of theslide bearing face 16 lying at between 60% and 90%, preferably between 60% and 80%, particularly preferably between 70% and 80%, of the circumferential extension U1 of theslide bearing face 16. - When the longitudinal central axis of the
axially extending groove 22, and therefore also groove 22, is situated in a portion of theslide bearing face 16 occupying such a position, segment flutter can be countered in a particularly effective manner. - For the ratio VU=U2/U1 between the circumferentially extending groove width U2 of the
axially extending groove 22 and the circumferential extension U1 of theslide bearing face 16 of therespective tilting segment 12, which circumferential extension U1 extends between thesegment leading edge 17 and thesegment trailing edge 18, the ratio is 0.02≦VU≦0.20, preferably 0.05≦VU≦0.20, particularly preferably 0.05≦VU≦0.10. - A
groove 22 with a groove width U2 of this kind has proven particularly advantageous for suppressing segment flutter. - In the embodiment example of
FIG. 2 , thegroove 22 extending in axial direction is bounded by four groove walls, namely by afirst groove wall 23 which extends in axial direction and faces thesegment trailing edge 18, asecond groove wall 24 which likewise extends in axial direction and is remote of thesegment trailing edge 18, and by twolateral groove walls first groove wall 23 and thesecond groove wall 24. The distance between thefirst groove wall 23 and thesecond groove wall 24, each of which extends in axial direction, determines the groove width U2 ofgroove 22, and the distance between thelateral groove walls groove 22 extending in axial direction. The ratio VL=L2/L1 between the axially extending groove length L2 of theaxially extending groove 22 and the axial extension L1 of theslide bearing face 16 extending between thelateral edges - In the variant in
FIG. 2 , theaxially extending groove 22, which is formed at theslide bearing face 16 of the tiltingsegment 12, is bounded on all sides bygroove walls groove 22 having a constant groove depth viewed in radial direction. -
FIG. 3 shows a further development of tiltingsegment 12 fromFIG. 2 . The variant inFIG. 3 differs from the variant inFIG. 2 in that afurther groove 27 is incorporated in theslide bearing face 16 of the tiltingsegment 12, namely, acircumferentially extending groove 27, which extends into theaxially extending groove 22 proceeding from thesegment leading edge 17. Oil can be conveyed from thesegment leading edge 17 into theaxially extending groove 22 via thisgroove 27 extending in circumferential direction. This causes a buildup of hydrodynamic pressure which, on the one hand, breaks up a pronouncedly laminar hot oil layer forming at the shaft surface of theshaft 13 in operation and, on the other hand, provides for a turbulent oil flow and possible Taylor vortices running in the rotating direction of theshaft 13 to be supported. Overall, this facilitates removal of heat from the slidingsurface 16 andshaft surface 13. - In the variant of
FIG. 3 , thisgroove 27 extending in circumferential direction runs into the center of the axial groove length L2 of thegroove 22 extending in axial direction. In contrast,FIG. 4 shows a further development of the invention in which thegroove 22 extending in circumferential direction runs adjacent to one of the lateral edges 19, 20 of theslide bearing face 16 and, in a lateral portion adjacent to alateral groove wall 25, runs into thegroove 22 extending in axial direction. - A further variant of a tilting
segment 12 is shown inFIG. 5 . InFIG. 5 , there is only thegroove 22 extending in axial direction but no groove extending in circumferential direction. Rather, thegroove 22 extending in axial direction is characterized by a bevel, namely such that proceeding from thegroove wall 24 remote of thesegment trailing edge 18, the groove depth ofgroove 22 increases in direction of thegroove wall 23 facing thesegment trailing edge 18. - In this respect, the groove depth according to the illustration in
FIG. 5 preferably ramps up linearly, i.e., steadily or continuously, in direction of thegroove wall 23 facing thesegment trailing edge 18. - Alternatively, the bevel can also be constructed with a radius.
- The supply of oil into the
axially extending groove 22 can be reinforced in this way so as to break up hot oil layers in the region of the shaft surface of theshaft 13 to be supported and, on the other hand, to generate a possible turbulent oil flow and Taylor vortices running in the rotating direction of theshaft 13 to be supported in order in this way ultimately to improve the transfer of heat and, therefore, the removal of heat from thesegment 12 and the supportedshaft 13. - It is also possible to combine this type of bevel of the
groove 22 extending in axial direction according toFIG. 5 with agroove 27 extending in circumferential direction according toFIGS. 3 and 4 . - By the invention, segment flutter of tilting
segments 12 can be effectively and reliably countered. Further, the transfer of heat from the lubricating gap can be improved and the temperature level can accordingly be lowered. - The present invention is directed not only to a
tilting segment 12 but also to ashaft bearing device 10 with at least onetilting segment 12 of this kind. - In operation, first tilting segments, which may be formed as tilting
segments 12, of theshaft bearing device 10 are more highly loaded by forces thansecond tilting segments 12. In ashaft bearing device 10 for a horizontally extending shaft, thelower tilting segments 12 in particular are more highly loaded by forces than theupper tilting segments 12. - Preferably, exclusively those tilting
segments 12, which are loaded relatively lightly by forces, i.e., exclusively at least one of thesecond tilting segments 12, are configured in the manner described with reference toFIGS. 2 to 5 . - Preferably, all of the second tilting segments which are loaded by forces to an extent below a limiting value are configured as described with reference to
FIGS. 2 to 5 . - The first tilting segments which are loaded by forces to an extent greater than the limiting value are preferably constructed in such a way that no grooves are incorporated in the
slide bearing face 16 thereof. - Thus, while there have shown and described and pointed out fundamental novel features of the invention as applied to a preferred embodiment thereof, it will be understood that various omissions and substitutions and changes in the form and details of the devices illustrated, and in their operation, may be made by those skilled in the art without departing from the spirit of the invention. For example, it is expressly intended that all combinations of those elements and/or method steps which perform substantially the same function in substantially the same way to achieve the same results are within the scope of the invention. Moreover, it should be recognized that structures and/or elements and/or method steps shown and/or described in connection with any disclosed form or embodiment of the invention may be incorporated in any other disclosed or described or suggested form or embodiment as a general matter of design choice. It is the intention, therefore, to be limited only as indicated by the scope of the claims appended hereto.
Claims (17)
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014000775.8A DE102014000775A1 (en) | 2014-01-24 | 2014-01-24 | Kipplagersegment for a shaft bearing device and shaft bearing device |
DE102014000775.8 | 2014-01-24 | ||
DE102014000775 | 2014-01-24 | ||
PCT/EP2015/000123 WO2015110267A1 (en) | 2014-01-24 | 2015-01-22 | Tilting segment for a shaft bearing device, and shaft bearing device |
Publications (2)
Publication Number | Publication Date |
---|---|
US20170009805A1 true US20170009805A1 (en) | 2017-01-12 |
US10408258B2 US10408258B2 (en) | 2019-09-10 |
Family
ID=52469786
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/113,685 Active US10408258B2 (en) | 2014-01-24 | 2015-01-22 | Tilting segment for a shaft bearing device, and shaft bearing device |
Country Status (7)
Country | Link |
---|---|
US (1) | US10408258B2 (en) |
EP (1) | EP3097316B1 (en) |
JP (1) | JP6553055B2 (en) |
KR (1) | KR101940385B1 (en) |
CN (1) | CN106062390B (en) |
DE (1) | DE102014000775A1 (en) |
WO (1) | WO2015110267A1 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11284813B2 (en) | 2016-11-16 | 2022-03-29 | Navix International Limited | Real-time display of tissue deformation by interactions with an intra-body probe |
US11622713B2 (en) | 2016-11-16 | 2023-04-11 | Navix International Limited | Estimators for ablation effectiveness |
US11631226B2 (en) | 2016-11-16 | 2023-04-18 | Navix International Limited | Tissue model dynamic visual rendering |
US11793571B2 (en) | 2016-11-16 | 2023-10-24 | Navix International Limited | Real-time display of treatment-related tissue changes using virtual material |
US11793576B2 (en) | 2015-05-12 | 2023-10-24 | Navix International Limited | Calculation of an ablation plan |
US12023091B2 (en) | 2021-01-04 | 2024-07-02 | Navix International Limited | Lesion assessment by dielectric property analysis |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016221044A1 (en) * | 2016-10-26 | 2018-04-26 | Robert Bosch Gmbh | tilting pad |
US10233970B2 (en) * | 2017-01-10 | 2019-03-19 | GM Global Technology Operations LLC | Journal bearings with surface features for improved bearing oil supply |
CN111771067B (en) * | 2018-03-15 | 2022-06-21 | 苏尔寿管理有限公司 | Bearing shell for tilt bearing shell thrust bearing assembly and thrust bearing assembly |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US64598A (en) * | 1867-05-07 | Cyeus tuckek |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2731305A (en) * | 1952-09-11 | 1956-01-17 | Gen Electric | High speed thrust bearing structure |
US3004804A (en) * | 1959-08-26 | 1961-10-17 | Gen Electric | Pivoted shoe bearing with force-feed lubrication |
US3339990A (en) * | 1964-07-13 | 1967-09-05 | Worthington Corp | Lubricated bearing shoe |
US3891281A (en) | 1974-04-08 | 1975-06-24 | Allis Chalmers | Pivoted pad bearing apparatus and method for bidirectional rotation |
US3887245A (en) * | 1974-04-08 | 1975-06-03 | Allis Chalmers | Pivoted pad bearing apparatus and method for bidirectional rotation |
JPS56141427A (en) | 1980-04-03 | 1981-11-05 | Shozo Kobayashi | Side-pull-type caliper brake for front wheel, with opening prevention device |
US4323286A (en) * | 1980-07-28 | 1982-04-06 | General Electric Co. | Thrust bearing cooling apparatus |
DE3117746A1 (en) * | 1981-05-05 | 1982-12-09 | Krupp Polysius Ag, 4720 Beckum | HYDRODYNAMIC RADIAL SLIDING BEARING |
JPS5846805U (en) * | 1981-09-25 | 1983-03-29 | 株式会社東芝 | Pad type journal bearing |
JPS6028494U (en) | 1983-07-29 | 1985-02-26 | クロイ電機株式会社 | Motor rotation speed control circuit |
JPH0231917U (en) * | 1988-08-24 | 1990-02-28 | ||
JPH09144750A (en) * | 1995-11-24 | 1997-06-03 | Kobe Steel Ltd | Pad type journal bearing |
US5772335A (en) | 1997-03-31 | 1998-06-30 | Whm Holding Company | Self-stabilizing, true-tilting pad with abruptly-stepped pocket for journal bearing |
US6499883B2 (en) * | 1997-03-31 | 2002-12-31 | Whm Holding Corporation | Tilting pad for bearings |
JP2001200847A (en) * | 1999-11-08 | 2001-07-27 | Mitsubishi Heavy Ind Ltd | Bearing device and turbine |
US6361215B1 (en) | 2000-03-03 | 2002-03-26 | Kingsbury, Inc. | Journal bearing |
US6485182B2 (en) | 2001-03-28 | 2002-11-26 | Rotating Machinery Technology, Inc. | Sleeve bearing with bypass cooling |
CN1776241A (en) * | 2005-12-15 | 2006-05-24 | 上海交通大学 | Integral multi-oil-wedge tiltable bush hydrodynamic sliding bearing |
JP2008151239A (en) | 2006-12-15 | 2008-07-03 | Mitsubishi Heavy Ind Ltd | Tilting pad type bearing |
CN101216065A (en) * | 2007-12-29 | 2008-07-09 | 东方电气集团东方汽轮机有限公司 | Ring shaped oil passage type tilting pad bearing |
WO2012114445A1 (en) * | 2011-02-21 | 2012-08-30 | 株式会社日立製作所 | Tilting pad journal bearing and rotary machine equipped with same |
DE102013211710C5 (en) * | 2013-06-20 | 2016-11-10 | Siemens Aktiengesellschaft | Wind turbine with a plain bearing |
-
2014
- 2014-01-24 DE DE102014000775.8A patent/DE102014000775A1/en not_active Withdrawn
-
2015
- 2015-01-22 EP EP15704203.7A patent/EP3097316B1/en active Active
- 2015-01-22 WO PCT/EP2015/000123 patent/WO2015110267A1/en active Application Filing
- 2015-01-22 JP JP2016544843A patent/JP6553055B2/en active Active
- 2015-01-22 US US15/113,685 patent/US10408258B2/en active Active
- 2015-01-22 KR KR1020167018595A patent/KR101940385B1/en active IP Right Grant
- 2015-01-22 CN CN201580005589.7A patent/CN106062390B/en active Active
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US64598A (en) * | 1867-05-07 | Cyeus tuckek |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11793576B2 (en) | 2015-05-12 | 2023-10-24 | Navix International Limited | Calculation of an ablation plan |
US11284813B2 (en) | 2016-11-16 | 2022-03-29 | Navix International Limited | Real-time display of tissue deformation by interactions with an intra-body probe |
US11622713B2 (en) | 2016-11-16 | 2023-04-11 | Navix International Limited | Estimators for ablation effectiveness |
US11631226B2 (en) | 2016-11-16 | 2023-04-18 | Navix International Limited | Tissue model dynamic visual rendering |
US11744515B2 (en) | 2016-11-16 | 2023-09-05 | Navix International Limited | Estimation of effectiveness of ablation adjacency |
US11793571B2 (en) | 2016-11-16 | 2023-10-24 | Navix International Limited | Real-time display of treatment-related tissue changes using virtual material |
US12023091B2 (en) | 2021-01-04 | 2024-07-02 | Navix International Limited | Lesion assessment by dielectric property analysis |
Also Published As
Publication number | Publication date |
---|---|
DE102014000775A1 (en) | 2015-07-30 |
CN106062390A (en) | 2016-10-26 |
KR101940385B1 (en) | 2019-01-18 |
WO2015110267A1 (en) | 2015-07-30 |
US10408258B2 (en) | 2019-09-10 |
KR20160097328A (en) | 2016-08-17 |
JP2017502232A (en) | 2017-01-19 |
CN106062390B (en) | 2019-11-19 |
EP3097316A1 (en) | 2016-11-30 |
EP3097316B1 (en) | 2019-06-05 |
JP6553055B2 (en) | 2019-07-31 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US10408258B2 (en) | Tilting segment for a shaft bearing device, and shaft bearing device | |
US7470064B2 (en) | Axial thrust bearing | |
US9169866B2 (en) | Tilting pad bearing | |
CN101809299B (en) | Hydrodynamic axial bearing | |
US8764296B2 (en) | Spiral-grooved thrust bearing | |
EP3032122B1 (en) | Tilting pad bearing | |
EP2896853B1 (en) | Slide part | |
US20150323000A1 (en) | Five-axial groove cylindrical journal bearing with pressure dams for bi-directional rotation | |
EP3032123B1 (en) | Tilting pad type journal bearing | |
EP2853789A1 (en) | Slide part | |
EP3112714A1 (en) | Spindle device | |
US8858081B2 (en) | Sliding bearing | |
US10415635B2 (en) | Tilting pad journal bearing | |
JP2013522561A (en) | Sliding bearing shell body | |
US10060470B2 (en) | Thrust bearing and rotary machine | |
JP2004293684A (en) | Thrust bearing | |
EP3051188B1 (en) | Sliding component | |
CN104169597A (en) | Axial sliding bearing | |
JP6200722B2 (en) | Tilting pad bearing device | |
WO2017104795A1 (en) | Slide bearing | |
KR20170122222A (en) | Sliding bearing | |
JP6724281B2 (en) | Plain bearing | |
JP2015187457A (en) | bearing member | |
US20160333925A1 (en) | Hydrodynamic Plain Bearing | |
JP2017110762A (en) | Slide bearing |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: MAN DIESEL & TURBO SE, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HAVLIK, NICO;LUTZ, MICHAEL;WACKER, CHRISTIAN;AND OTHERS;SIGNING DATES FROM 20160615 TO 20160627;REEL/FRAME:042754/0238 |
|
AS | Assignment |
Owner name: MAN ENERGY SOLUTIONS SE, GERMANY Free format text: CHANGE OF NAME;ASSIGNOR:MAN DIESEL & TURBO SE;REEL/FRAME:046818/0806 Effective date: 20180626 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: FINAL REJECTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: NOTICE OF ALLOWANCE MAILED -- APPLICATION RECEIVED IN OFFICE OF PUBLICATIONS |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: AWAITING TC RESP, ISSUE FEE PAYMENT VERIFIED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: PUBLICATIONS -- ISSUE FEE PAYMENT VERIFIED |
|
STCF | Information on status: patent grant |
Free format text: PATENTED CASE |
|
MAFP | Maintenance fee payment |
Free format text: PAYMENT OF MAINTENANCE FEE, 4TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M1551); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY Year of fee payment: 4 |